US4700772A - Heat exchanger system - Google Patents

Heat exchanger system Download PDF

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Publication number
US4700772A
US4700772A US06/752,394 US75239485A US4700772A US 4700772 A US4700772 A US 4700772A US 75239485 A US75239485 A US 75239485A US 4700772 A US4700772 A US 4700772A
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United States
Prior art keywords
duct
heat exchanger
duct part
hot gas
branch
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Expired - Fee Related
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US06/752,394
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English (en)
Inventor
Peter Baumberger
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ABB Management AG
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Gebrueder Sulzer AG
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Assigned to SULZER BROTHERS LIMITED reassignment SULZER BROTHERS LIMITED ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BAUMBERGER, PETER
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Publication of US4700772A publication Critical patent/US4700772A/en
Assigned to SULZER AG reassignment SULZER AG CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SULZER BROTHERS LIMITED
Assigned to ABB MANAGEMENT LTD. reassignment ABB MANAGEMENT LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SULZER AG
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F22B21/22—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes of form other than straight or substantially straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1838—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines the hot gas being under a high pressure, e.g. in chemical installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/007—Control systems for waste heat boilers

Definitions

  • This invention relates to a heat exchanger system. More particularly, this invention relates to a heat exchanger system for removing heat from a hot process gas.
  • European Patent Application No. 0111615 describes a heat exchanger system which is comprised of a number of heat exchanger surfaces which are received in a single substantially cylindrical pressure vessel.
  • a duct part is disposed in the pressure vessel to contain one of the heat exchanger surfaces while a pair of parallel branch ducts extend from the duct part into a common mixing chamber.
  • an evaporator heating surface is also disposed in one of the branch ducts as a second heat exchanger surface.
  • an adjustable restrictor is disposed in one of the branch ducts in order to control the gas flow.
  • Such a heat exchanger system is of compact construction and is readily adjustable.
  • the above type of system has limited usefulness.
  • the invention provides a heat exchanger system for removing heat from a hot gas which is comprised of a pressure vessel, a first duct part within the vessel for conveying a hot gas therethrough, a pair of parallel branch ducts communicating with the duct part in order to convey the hot gas therethrough and a common mixing chamber communicating with the branch ducts in order to receive the hot gas.
  • a first evaporator heating surface is disposed in one of the branch ducts for conveying a working medium therethrough in heat exchange relation with the hot gas in the branch duct.
  • an adjustable restrictor is disposed in at least one of the branch ducts for controlling a flow of hot gas therethrough.
  • a second duct part is disposed in the vessel in communication with and downstream of the mixing chamber for conveying the hot gas therethrough and a heat exchanger surface is disposed in the second duct part for conveying a working medium therethrough in heat exchange relation with the hot gas.
  • the provisions of a second duct part in which a second heat exchanger surface is disposed facilitates the transmission of very substantial quantities of heat even without the need for the provision of a heat exchanger surface in the second branch duct.
  • the second branch duct can, if required, serve simply as a hot gas bypass. The control range of the system is therefore increased considerably as compared with the known system.
  • a heat exchanger surface in the second branch duct can be of small dimensions or possibly completely omitted, the junction zone between the first duct part and the branch ducts does not have to be so resistant to high temperatures whereas the second heat exchanger surface in the second duct part is acted on only by gas which has been adequately cooled in the first branch duct at least along the entire evaporator heating surface.
  • the second branch duct need have only a relatively small heat exchange surface or, in some circumstances, no such surface at all. There are fewer restrictions on the construction of the second branch duct since the duct can be disposed even at the center of the pressure vessel. This serves to facilitate endeavors for the system to be of compact construction.
  • the system may be constructed so that the first duct part, at least one of the branch ducts and the second duct part are annular ducts which are coaxial of the pressure vessel. This leads to an optimal use of the space occupied by the heat exchanger system and therefore to a smaller and relatively light pressure vessel. This results in a lower cost, ready transportability and ready assembly of the system.
  • the system may also comprise a second evaporator in the first duct part which communicates with the evaporator in the branch duct in order to convey a common working medium. This permits a substantial increase in the temperature range with which the heat exchanger system can operate.
  • the first duct part and the first branch duct may also be disposed in axial alignment with each other. This provides constructional advantages because smooth partitions can be provided. This, in turn, facilitates easy dismounting of the very heavily stressed heating surfaces.
  • the second branch duct may be a cylindrical duct with a displacement member arranged centrally in the first duct part coaxial of the first branch duct.
  • each tube bank may be involute with arms parallel to the vertical axis of the vessel. This provides particular cost advantages since the pipe coils are very simple to produce and the suspension of such tube banks requires no special carrying or support means.
  • the heat exchanger surface in the second duct part may be formed of a helical tube heating surface. This permits a very high heat transfer and, in the event of a leak, the leaky pipes can be readily cut out of operation without leading to hot strands in the gas.
  • the restrictor may be in the form of a centrally disposed mushroom valve downstream of the cylindrical branch duct. This provides a simple and relatively small restrictor which is disposed in a relatively cool zone and which is simple to operate.
  • the pressure vessel may be provided with a coaxial hot gas entry at a bottom and at least one lateral gas outlet connection at the top.
  • the gas outlet connection has to be disposed in the bottom part of the pressure vessel so that the connections of all the heat exchanger surfaces to the medium-conveying lines must be disposed in the top part of the pressure vessel.
  • at least the medium connections of the bottom heat exchanger surface are disposed in the bottom part of the pressure vessel.
  • An annular chamber may also be disposed between the second duct part and a wall of the pressure vessel while communicating the second duct part with the gas outlet connection. This provides a simple means of protecting the pressure vessel wall against overheating.
  • a second adjustable restrictor may also be provided for selectively connecting the gas outlet connection with at least one of the duct parts and /or the branch ducts. This provides a simple means of controlling the final temperature of the gas.
  • the tube banks for the evaporator may also have arms of reduced diameter to define the second evaporator, that is, the evaporator in the first duct part. This has the advantage of reducing the temperature of the coiled tube banks. Also, a cross-flow of some of the gas is permitted in the junction region without a high pressure drop on the gas side.
  • the coil tubes may also be spaced apart from one another by projections. This enables the coiled tubes to be packed together to form a compact ring bunch which can be readily suspended by way of the outermost tubes.
  • a cover may also be secured to the top of the pressure vessel with a layer of thermal insulation on the underside.
  • the cover ensures ready accessibility to the interior of the pressure vessel and particularly to the heating surfaces while the insulation permits a relatively thin-walled cover to be used.
  • FIG. 1 illustrates a fragmented diagrammatic view in vertical section through a heat exchanger system constructed in accordance with the invention
  • FIG. 2 illustrates a view to a larger scale than FIG. 1 of a section taken on line II--II of FIG. 1;
  • FIG. 3 illustrates a developed view of a coiled tube tank.
  • the heat exchanger system is constructed to remove heat from a hot gas such as a process gas.
  • the system includes a cylindrical pressure vessel 1 which has a tubular bottom part 2 which is carried by way of lug supports 3 on a foundation 4.
  • the bottom part 2 has a coaxial hot gas entry at a bottom end which is connected to a suitable gas entry line (not shown).
  • at least one lateral gas outlet 5 is provided at the top of the vessel 1 slightly below the top end of the part 2.
  • a flange 6 is provided at the top end of the part 2 and a cover 7 rests on the flange 6 to form a top part of the vessel 1.
  • a layer of thermal insulation 8 is provided on the underside of the cover 7.
  • a lining 10 extends at a reduced distance from the inner wall of the vessel part 2 so as to bound an annular chamber 9.
  • the lining 10 extends over a central extended zone of the part 2 and terminates at the top at an inside edge of an annular plate 12 to which the lining 10 is sealingly connected.
  • the periphery of the plate 12 is also sealingly connected to the vessel part 2.
  • An outer duct wall 20 extends inside the lining 10 at a reduced radial distance to define an annular space therebetween.
  • a middle duct wall 22 is also disposed inside the outer wall 20 and is connected at the bottom end by way of a seal-tight but readily releasable connection 16 to the wall of the vessel part 2.
  • An inner duct wall 28 is provided inside duct wall 22 and cooperates therewith to bound a first branch duct 32 of annular cross-section.
  • the wall 28 also bounds a cylindrical inner second branch duct 33 and carries a metal cone 23 having a valve seat 24 at the top end.
  • An adjustable restrictor 25 in the form of a centrally disposed mushroom valve is provided above the valve seat 24 for controlling a flow of hot gas therethrough. As indicated, the restrictor 25 is actuated by a servomotor 26.
  • a displacement member 14 is disposed centrally within and in the bottom part of the wall 22 and cooperates with the wall 22 to bound a duct part 30. As indicated, the displacement member is coaxial of the duct part 30. In addition, a junction is disposed above the member 14 at which the two branch ducts 32, 33 start. As shown, the duct part 30 and the outer branch duct 32 are in alignment with one another.
  • a heating surface 36 in the form of an evaporator extends over the whole height of the annular chamber formed by the duct part 30 and the first branch duct 32.
  • the heating surface 36 is formed of thirty six involute single coiled tube banks 38 each of which is formed by a tube with vertical arms.
  • a tube bank 28 is shown in developed form in FIG. 3 and is disposed as indicated in FIG. 2.
  • Each tube bank 38 has an inlet arm 51 which extends on an outermost tube cylinder 50 (see FIG. 3) and which is connected by way an inclined part 52 to an arm 54 which extends on an innermost tube cylinder 53 (see FIG. 3).
  • the arm 54 is, in turn, connected at the top by way of a bend to an arm 55 which is connected at the bottom by way of a bend to another parallel arm 56.
  • an outlet arm 57 After multiple meandering of the tube, an outlet arm 57 finally extends vertically upwards and leads together with the arm 51 through the cover 7 by way of seal-tight tubes (see FIG. 1).
  • the arms 51, 57, together with the corresponding arms of the other thirty five tube banks 38 are then connected to a distributor 58 and a header 59, respectively.
  • the tube arms are spaced apart from one another either by projections (not shown) disposed on the arms or by peripheral ribs or fins or the like disposed at various heights.
  • the banks 38 are layered on the inner duct wall 28, bent into involute surfaces and pressed together radially by means of clamping bands (not shown) which extend over the periphery of the surface 36.
  • the resulting heating surface bunch is encased in wire braiding near the first branch duct 32.
  • the outermost arms 51 can engage the central duct wall 22, the same thus being cooled in operation.
  • wire braiding possibly in a number of layers, made of a highly heat resistant material can be provided or an insulation can be provided which reduces heat transfer to the central duct wall 22.
  • the annular chamber bounded by the outer duct wall 20 and middle duct wall 22 forms a second duct part 34 in which a second heat exchanger surface 62--a superheating surface in this case--is disposed.
  • This surface 62 is embodied by twenty-nine helically extending tubes 64 which form five tube cylinders. At their bottom end, the tubes 64 are connected to distributors 75, 75' by way of connecting tubes 72, 72' which extend through the wall of the part 2 of the vessel 1. At the top end, each tube 64 is connected by way of a tube bend 65 to one of twenty-nine fallers 66 which extend vertically in the annular duct between the lining 10 and the outer duct wall 20.
  • the fallers 66 issue from the annular duct by way of a substantially gas-tight lead-through (not shown) and issue laterally from the pressure vessel 1 through the wall of the part 2 in thermosleeves.
  • the fallers 66 are connected to two headers 70, 70'. As such, the surface 62 is free to expand upwardly.
  • the tubes 64 of the surface 62 are retained in perforate support plates 61 disposed inside the second duct part 34 in three planes which are offset from one another and which extend through the vertical axis of the vessel 1.
  • the bottom ends of the plates 61 are secured laterally to the wall of the part 2 and the support plates 61 are formed over the height of the surface 62 with bores 63 as shown in FIG. 2.
  • the tubes 64 extend sinuously in the bores 63 and, the plates 61 are free to expand upwardly.
  • An adjustable restrictor in the form of a valve comprising a handwheel 80, a horizontal valve rod 81 and a cone 82 operative in a circular aperture in the lining 10 is disposed above the gas outlet connection 5 on the vessel part 2.
  • the wheel 80 is outside the vessel 1 and, the rod 81 extends through the wall of the vessel part 2.
  • a screwthread (not shown) on the rod 81 is engaged in a nut 83 secured to the vessel part 2 and the place where the rod 81 extends through the bottom part 2 is sealed in known manner. This restriction serves to selectively connect the gas outlet 5 with the second duct part 34.
  • the gas outlet connection 5 is lined with a lining plate 92 which forms an inlet nozzle and which extends into a static mixer 93.
  • connection 16 and the lowest part of the part 2 are protected against overheating by masonry 76 which can comprise cooling tubes (not shown).
  • the header 59 is connected by way of a wet steam line 45 to a separator 46 whose steam outlet line 47 extends to the distributors 75, 75' while separated water discharges through a discharge connection 48 at the base of the separator 46. Also connected to the distributors 75, 75' is another steam supply line 49 coming, for instance, from coolers or from a boiler installation.
  • the heat exchanger system shown in FIGS. 1-3 operates as follows:
  • a process gas at a temperature of, for example, 1000° C. and at a pressure of from 20 to 40 bar is supplied to the bottom end of the vessel 1. This gas flows through the duct part 30 and then, after cooling to approximately 900° C., is distributed through the first branch duct 32 and second branch duct 33. The partial flow in the duct 32 yields further heat and is cooled, for example, to 600° C.
  • the combined gas flow then passes downwardly into the second duct part 34, and is further cooled, for example, to 400° C.
  • the gas then passes upwardly through the annular chamber 9 to cool the wall of the pressure vessel 1, into the annular chamber below the plate 12 and thence through the gas outlet connection 5 for further use.
  • the lining plate 92 keeps such streaks away from the pressure-bearing wall.
  • the static mixer 93 then equalizes the gas temperature.
  • the heat exchanger system is supplied by way of the distributor 58 with a secondary medium in the form of preheated water injected into the surface 36 through the arms 51.
  • a secondary medium in the form of preheated water injected into the surface 36 through the arms 51.
  • the surface 36 serves as an evaporator, and so the mixture of steam and water flows through the arms 57 into the header 59.
  • the mixture is then separated in the separator 46, water discharging through the connection 48 while wet steam is injected through the line 47 into the distributors 75, 75'.
  • wet steam from the plant can be injected into the distributors 75, 75' through the line 49.
  • the wet steam passes through the fallers or connecting tubes 72, 72' into the second heat exchanger surface 62 and is superheated therein in countercurrent to the heating gas.
  • the superheated steam leaves the heat exchanger through the tubes 66 and headers 70, 70'.
  • the heating surfaces in the duct part 30 and in the first branch duct 32 are large enough for operations to begin with the restrictor 25 and cone 82 fully open.
  • Considerable heat is evolved in the duct part 30 in these circumstances and a very large proporation of the gas leaving the part 30 goes through the second branch duct 33, hence the quantity of heat evolved in the first branch duct 32 stays relatively smaller.
  • the gas entry temperature in the second branch duct 33 is already fairly low, there is no risk of the duct 33 overheating.
  • the gas temperature downstream of the second duct part 34 is relatively low. The temperature of the gas issuing from the pressure vessel 1 can be restored to the required level by the injection of a relatively large quantity of hot gas through the fully open valve cone 82.
  • Soiling of the surface 36 reduces its heat uptake. This reduction can be corrected by reducing the opening cross-section of the restrictor 25. Since the second heat exchanger surface 62 is also substantially over-dimensioned, there is little risk in these circumstances of the required superheat temperatures of the steam not being reached.
  • the tube banks 38 can readily be bent outwards for cleaning.
  • the surface 62 can be inspected from the inside and cleaned from the inside.
  • junction If the junction be too low or too high due to design, it is a simple matter to shorten the inner duct wall 28 or extend the wall 28 downwardly. Another possibility is to make the junction adjustable, for example, by one or two sleeve valves or by a bypass in the wall 28.
  • the invention is not limited to the embodiment shown.
  • the duct walls 20, 22, 28 may be devised at least to some extent as diaphragm walls--i.e., as walls of welded tubes.
  • the heat exchanger surfaces of the embodiment are shown in a very simple form. They can, however, be subdivided. The flow directions can also be wholly or partly reversed.
  • More than one secondary medium can participate in the heat exchange. If it is required to obviate restrictors in the pressure vessel, the restrictors can be placed in connecting lines serving to convey gas outside the pressure vessel.
  • the type of heat exchanger surfaces may also be, for instance, blind tubes or heat tubes.
  • the branching into branch ducts can be staggered at various temperatures or for various temperature ranges.
  • the recombination of the branch flows can be staggered.
  • the opening controlled by the valve cone 82 can also be connected on the inlet side to places in either branch duct.
  • the arrangement of the ducts in the pressure vessel may be changed over or arranged in any other way.
  • the part 2 of the pressure vessel 1 may be subdivided below the securing place of the plates 61 by horizontal intermediate flanges.
  • valve cones 82 and the components associated therewith can be provided.
  • the invention thus provides an improved heat exchanger system for removing heat from a hot process gas.
  • the invention further provides a means of modifying existing heat exchanger systems in a relatively simple manner for improved operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US06/752,394 1984-07-05 1985-07-03 Heat exchanger system Expired - Fee Related US4700772A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3253/84 1984-07-05
CH3253/84A CH665274A5 (de) 1984-07-05 1984-07-05 Waermeuebertrager.

Publications (1)

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US4700772A true US4700772A (en) 1987-10-20

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ID=4251966

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US06/752,394 Expired - Fee Related US4700772A (en) 1984-07-05 1985-07-03 Heat exchanger system

Country Status (6)

Country Link
US (1) US4700772A (ja)
EP (1) EP0166805B1 (ja)
JP (1) JPS6124988A (ja)
CA (1) CA1248083A (ja)
CH (1) CH665274A5 (ja)
DE (1) DE3475646D1 (ja)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050103484A1 (en) * 2001-12-25 2005-05-19 Haruhiko Komatsu Heat exchanger
US20080282996A1 (en) * 2007-05-15 2008-11-20 Combustion & Energy Systems Ltd. Reverse-Flow Condensing Economizer And Heat Recovery Method
US20090041642A1 (en) * 2007-08-07 2009-02-12 General Electric Company Radiant coolers and methods for assembling same
US20090038155A1 (en) * 2007-08-07 2009-02-12 Judeth Helen Brannon Corry Syngas coolers and methods for assembling same
US20090087707A1 (en) * 2007-10-01 2009-04-02 Snecma Preheating heat exchanger for a fuel cell
US20160033211A1 (en) * 2014-07-31 2016-02-04 Halla Visteon Climate Control Corp. Oil cooler
US9291401B2 (en) 2014-02-24 2016-03-22 Combustion & Energy Systems Ltd. Split flow condensing economizer and heat recovery method
EA033825B1 (ru) * 2017-11-03 2019-11-29 Non Profit Joint Stock Company Almaty Univ Of Power Engineering And Telecommunications Комбинированный теплообменник

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1188371A (fr) * 1957-12-16 1959-09-22 Alsthom Cgee Chaudière de récupération
US3433298A (en) * 1966-05-03 1969-03-18 Schmidt Sche Heissclampf Gmbh Heat exchanger especially for the cooling of hot gases
US3753662A (en) * 1966-10-18 1973-08-21 Montedison Spa Synthesis reactor with particular cooling means for exothermic reactions at high pressure
US3871444A (en) * 1971-08-02 1975-03-18 Beckman Instruments Inc Water quality analysis system with multicircuit single shell heat exchanger
US3991821A (en) * 1974-12-20 1976-11-16 Modine Manufacturing Company Heat exchange system
US4047506A (en) * 1974-12-06 1977-09-13 Sulzer Brothers Limited Gas heated steam generator
DE2846455B1 (de) * 1978-10-23 1979-10-31 Borsig Gmbh Rohrbuendel-Waermetauscher mit gleichbleibender Austrittstemperatur eines der beiden Medien
US4173997A (en) * 1977-02-23 1979-11-13 Westinghouse Electric Corp. Modular steam generator
US4285393A (en) * 1978-10-26 1981-08-25 Ght, Gesellschaft Fur Hochtemperaturreaktor-Technik Mbh Heat exchanger for high-temperature gases
US4494484A (en) * 1982-11-24 1985-01-22 Sulzer Brothers Limited Heat exchanger for a process gas
US4498524A (en) * 1977-08-08 1985-02-12 Jacobsen Orval E Heat exchanger with by-pass
US4502626A (en) * 1980-05-16 1985-03-05 Gas Research Institute Combustion product condensing water heater

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH174774A (de) * 1934-06-08 1935-01-31 Sulzer Ag Wärmeaustauscher.
AT278862B (de) * 1967-08-24 1970-02-10 Waagner Biro Ag Gasbeheizter Wärmetauscher
DE3137576C2 (de) * 1981-09-22 1985-02-28 L. & C. Steinmüller GmbH, 5270 Gummersbach Vorrichtung zum Abkühlen von aus einem Vergasungsprozeß stammenden Prozeßgas

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1188371A (fr) * 1957-12-16 1959-09-22 Alsthom Cgee Chaudière de récupération
US3433298A (en) * 1966-05-03 1969-03-18 Schmidt Sche Heissclampf Gmbh Heat exchanger especially for the cooling of hot gases
US3753662A (en) * 1966-10-18 1973-08-21 Montedison Spa Synthesis reactor with particular cooling means for exothermic reactions at high pressure
US3871444A (en) * 1971-08-02 1975-03-18 Beckman Instruments Inc Water quality analysis system with multicircuit single shell heat exchanger
US4047506A (en) * 1974-12-06 1977-09-13 Sulzer Brothers Limited Gas heated steam generator
US3991821A (en) * 1974-12-20 1976-11-16 Modine Manufacturing Company Heat exchange system
US4173997A (en) * 1977-02-23 1979-11-13 Westinghouse Electric Corp. Modular steam generator
US4498524A (en) * 1977-08-08 1985-02-12 Jacobsen Orval E Heat exchanger with by-pass
DE2846455B1 (de) * 1978-10-23 1979-10-31 Borsig Gmbh Rohrbuendel-Waermetauscher mit gleichbleibender Austrittstemperatur eines der beiden Medien
US4285393A (en) * 1978-10-26 1981-08-25 Ght, Gesellschaft Fur Hochtemperaturreaktor-Technik Mbh Heat exchanger for high-temperature gases
US4502626A (en) * 1980-05-16 1985-03-05 Gas Research Institute Combustion product condensing water heater
US4494484A (en) * 1982-11-24 1985-01-22 Sulzer Brothers Limited Heat exchanger for a process gas

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050103484A1 (en) * 2001-12-25 2005-05-19 Haruhiko Komatsu Heat exchanger
US8006651B2 (en) 2007-05-15 2011-08-30 Combustion & Energy Systems Ltd. Reverse-flow condensing economizer and heat recovery method
US20080282996A1 (en) * 2007-05-15 2008-11-20 Combustion & Energy Systems Ltd. Reverse-Flow Condensing Economizer And Heat Recovery Method
WO2008138128A1 (en) * 2007-05-15 2008-11-20 Combustion & Energy Systems Ltd. Reverse-flow condensing economizer and heat recovery method
US20090041642A1 (en) * 2007-08-07 2009-02-12 General Electric Company Radiant coolers and methods for assembling same
US20090038155A1 (en) * 2007-08-07 2009-02-12 Judeth Helen Brannon Corry Syngas coolers and methods for assembling same
US8191617B2 (en) 2007-08-07 2012-06-05 General Electric Company Syngas cooler and cooling tube for use in a syngas cooler
US8240366B2 (en) * 2007-08-07 2012-08-14 General Electric Company Radiant coolers and methods for assembling same
US20090087707A1 (en) * 2007-10-01 2009-04-02 Snecma Preheating heat exchanger for a fuel cell
US8153317B2 (en) * 2007-10-01 2012-04-10 Snecma Preheating heat exchanger for a fuel cell
US9291401B2 (en) 2014-02-24 2016-03-22 Combustion & Energy Systems Ltd. Split flow condensing economizer and heat recovery method
US20160033211A1 (en) * 2014-07-31 2016-02-04 Halla Visteon Climate Control Corp. Oil cooler
US9897397B2 (en) * 2014-07-31 2018-02-20 Hanon Systems Oil cooler
EA033825B1 (ru) * 2017-11-03 2019-11-29 Non Profit Joint Stock Company Almaty Univ Of Power Engineering And Telecommunications Комбинированный теплообменник

Also Published As

Publication number Publication date
EP0166805B1 (de) 1988-12-14
CH665274A5 (de) 1988-04-29
DE3475646D1 (en) 1989-01-19
EP0166805A3 (en) 1986-04-09
EP0166805A2 (de) 1986-01-08
CA1248083A (en) 1989-01-03
JPS6124988A (ja) 1986-02-03

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